Pump or motor



July 18, 1939. E. BENEDEK 2,166,717

PUMP OR MOTOR Filed March 20, 1934 4 SheetsSheet 2 y '1 1939- E. BENEDEK 2,166,717

PUMP 0R MOTOR Filed March 20, 1954 4 Sheets-Sheet s I w 3mm /f Em 1 4 July 18, 1939. E. B IENEDEK 2,166,717

PUMP OR MOTOR Filed March 20, 1934 v 4 Sheets-Sheet 4 Patented July 18, 1939 UNITED STATES- PATENT OFFICE 13 Claims.

This invention relates to pumps or motors of the radial multi-plunger or piston variable displacement type and its use is adapted primarily to reversible high pressure fluid transmission.

Pumps of the type referred to ordinarily comprise a'rotary barrel with a radial arrangement of cylinders as the driving member, a co-rotating piston actuating reaction member surrounding said driving member, a plurality of radial plungers or pistons carried by said driving member and arranged to be actuated by the said co-rotating.

member and the driving member. Usually the driving connection is afforded by a plurality of sliding reciprocating frictionally operated cross heads or shoes. The shoes and/orcro heads are either attached to the outer end of t e pistons by journal pins or are rigidly secured to the piston heads and guided for reciprocatory movement in appropriate grooves in an oil drum 2 forming part of the piston actuating reaction member.

As heretofore designed, commercial forms of pumps also include axially spaced circular flanged members forming part of the oil drum and mounting means for separate bearing members to support the drum at its axial extremities. In order to lubricate the sliding attachments or connections of the pistons the drum must be supplied with lubricating fiuid from the slippage of the pump and since the slippage occurs at high pressure, temperatures also run high.

One object of the present invention is the provision of a pump of the general type above described which is so designed as to make possible the elimination of sliding cross head blocks and shoes and dispensing entirely with the high temperature lubricating container such as the rotary drums heretofore required.

Another object is the provision of a pump of the same type, the elements of which are so arranged as to greatly reduce the inertia of the pistons and thereby reduce the tendency of the pistons to eccentrically wear the cylinder walls; in other words, to cause the cylinder walls to become out of round as in many pumps of this type heretofore known.

Another object is the provision of special torque or torquetransmitting members between the piston cylinder barrel and the actuating and reaction member or members to thereby relieve the piston and cylinder assemblage from flexing strains.

A further object isthe provision of a simple and effective means for supporting the reaction member or members in such manner as to greatly reduce or eliminate noise and vibration from the mechanism.

Another object is the provision of a novel means to couple the piston, cylinder, barrel and co-rotating reaction member or members both for better starting operation and better normal running operations.

A further general object is the provision of a pump or motor of the character above described which shall have substantially a minimum number of parts, substantially maximum rigidity, which will be foolproof in operation, as nearly fully frictionless as possible, the parts of which may be easily interchanged so that defective or worn parts after years of service or breakage may be replaced in the field without requiring complete disassemblage ofthe mechanism or sending the same to a repair shop for expert attention and repair.

A further object is the design of a pump in which all the supported spans of the necessary heavier moving parts and assemblies are reduced substantially to a minimum to thereby eliminate mechanical stresses between the pumping elements as much as possible and further to maintain accuracy of operation of the pump and associated elements for a longer period of time as compared to pumps heretofore known.

A further object is the provision of a pump so designed as to obviate the necessity for a high temperature oil bath surrounding the working parts and preventing the cooling of the parts by heat dissipation both through radiation and the heat conductivity of the metal composing such parts, all to the general end that the pump will operate at lower temperatures and maintain a predetermined pressure at a lower viscosity of the working medium,-oil, e. g.

Other objects and features of the invention will become apparent from the following description of the illustrated embodiments.

In the drawings:

Fig. 1 is a longitudinal substantially central sectional view of a pump or motor constructed in accordance herewith, the section being on the line l-l of Fig. 2;

Fig. 2 is a transverse sectional view taken substantially on the line 2-2 of Fig., 1, a portion, however, being broken away along the line 2z2r on Fig. 1;

Fig. 3 is a sectional view similar to Fig. 2 taken partly along the line 2-4 on Fig. 1 and partly along the line 3-3 on Fig. 1;

Fig. 4 is a fragmentary sectional view taken substantially along the line 4-4 on Fig. 1;

Fig. 5 is a view corresponding generally to Fig. 4 but showing certain modifications of the driving, coupling elements between the pistons and co-rotating reaction members;

Fig. 6 shows a flexible connection between piston and associated driving head, the latter being shown in central longitudinal cross section;

Fig. '7 is a side elevation of a modified form of piston taken normal to its axis;

Fig, 8 is a fragmentary side elevationof the part shown in Fig. 7 taken normal to the axis of the piston and at right angles to Fig. '7;

Fig. 9 is a view corresponding substantially to Fig. 8, the upper end of the piston, however, being shown broken away in central longitudinal section;

Fig. 10 is a central axial sectional view of a modified piston actuating assembly and Fig. 11 is a transverse sectional view taken substantially along the line l on Fig. 10.

Referring in detail to the drawings and first to Fig. 1, the main driving element of the pump comprises, as shown, an impeller shaft which may be suitably driven electrically or mechanically in any convenient manner, not shown. The impeller shaft I is connected to one end of a rtary impeller in the form of a piston carrying barrel 5, preferably by a tapered fit connection 3 and feather key 4. The tapered bore in the barrel 5 is machined to accurately fit the taper of the shaft and a suitable lock nut 6 is threaded onto the shaft as at 2 to draw the tapered surfaces together and firmly lock the shaft and barrel to turn as a unit.

The rotary impeller or piston carrying barrel 5 is primarily mounted in the pump casing to be hereinafter described and is also mounted for relative rotation with respect to a fixed pintle I4 extending axially into the barrel at its central portion. The pintle l4 has an enlarged cylindrical shank portion, as at |5, which passes through a counter bore It] at the end 9 of the barrel and is rigidly secured as by heavy hydraulic press fit into a central bore of the hub portion 20' of a bell-shaped end plate 20 forming part of the main casing. The main pump connections, not shown, are located in the hub portion 20 and communicate with respective aligned openings, indicated. at l8 and IS, in the pintle.

The counter bore l0 forms a cup-shaped hollow space between the end 9 of the barrel 5 and the pintle shank so that the free or working end only of the pintle is in working sliding contact with the barrel and only for a short distance along the same and midway between the supports of the barrel. The projection of the heavy section of the pintle into the enlarged bore of the barrel minimizes as much as possible the deflection of the reduced portion of the pintle in the bore of the barrel under load. Further, by reason of the clearance at ||l||, the friction between the barrel and pintle is minimized and this is particularly important in the zone of the bearing 3| (to be hereinafter described) which under certain conditions of heat might contractthe barrel at said zone. The free uninterrupted clearance space or void intervening between the pintle shank and the inner end wall of thebarrel counterbore is provided as a result of the shanks terminating short of the end of the counter-bore. The coacting valve portions of the barrel bore and pintle lie entirely between the planes of the sets of bearings 3| and 3|, having just suflicient axial length to seal the pressure fluid by the viscosity of the latter in the close running fit between the telescoping smaller diameter parts of the pintle and barrel and the unbalanced hydrostatic pressure built up by the high pressure 011 film at one side of the pintle, during action of the pump, is minimized. The clearance space l0 moreover, provides for the relief of escaping high pressure slip fluid from between the reduced portion of the pintle and the coacting bore of the barrel 5 and, further by reducing the area of surface fit between the pintle and barrel, the actual fitting operation between the pintle and barrel may be effected more accurately. With the contacting surface areas reduced it is possible to provide an almost perfect hydraulic fit between the parts just referred to, thus allowing the proper lubrication necessary for smooth operation of the co-acting parts but preventing the escape of undue amounts of working fluid at high pressure. A similar clearance space Ha is provided between the free end of the pintle and the barrel and drive shaft portion 3 which may, if desired, be vented into the outer portions of the casing by radial holes in the barrel, not illustrated.

In order to maintain the desired concentric relation between the central valve portion of the barrel 5 and the reduced portion of the pintle l4 at the maximum operating pressure and in order to eliminate twist and deflection in the barrel under maximum driving torque and full pressure and at the maximum spread of the hydrostatic force which may impose several tons of load on the co-acting portions of the barrel 5 and pintle l4 and cause undue friction and wear therebetween, I form the rotary impeller barrel 5 of rigid substantially uniform cross section throughout substantially its entire length. The central portion of the barrel, which has material cut therefrom to form the radial cylinders, has a cylindrical spider flange I to be hereinafter described, this flange compensating for the material removed and serving other functions to be later described. At the end portions of the barrel 5 I provide relatively large and sturdy antifriction bearings 3| and 3|, the outer races of which are supported in the bell-shaped end plates of the housing. The end plate 20 has been previously described and the end plate 22 is of similar construction, the two plates being rigidly secured to a central cylindrical body or ring 2|. The outer marginal edges of both plates are shouldered to receive the ring in conventional fashion. Both the inner and outer races 2929' and 30-30 of each set of bearings are identical in size forminimizing twist, that is, unequal torsional resistance to rotation of the barrel. Both inner rings axially abut shoulders on the barrel and the outer rings are firmly seated axially against oppositely disposed shoulders on the plates 20 and 22 with the result that, assuming there is no play between the balls 3| and 3| and the respective races, there will be no end play on part of the barrel 5. Since the pistons are disposed equal distances from both sets of bearings 3| and 3| the hydrostatic load is exerted equally on the two sets of bearings. By reason of the symmetrical construction of the barrel 5 and its mountings on each side of the center of pressures and by reason of the ruggedness of construction including the heavy bearings and heavy uniform cross section of the barrel, the arrangement resists to the greatest possible degree all forces tending to wear, collapse or deflect the barrel and associated parts.

The impeller or cylinder barrel 5 is provided with a pluraltiy of radial cylinder bores 3, five being shown, which are placed successively in communication with the pump ports l3 and I1 through reduced openings l2 aligned with the cylinder bores.

The arrangement as will hereinafter be more fully understood is such that the ports l6 and I! are sometimes discharge ports and sometimes intake ports, this depending upon the setting of the piston actuating and reaction members to be hereinafter described. It will be seen from Figs. 1 and 3, particularly, that the flange I is in the transverse plane of the bores l3 and forms a reinforcement for the cylinder barrel where some material is removed therefrom to form the cylinders.

It is evident from Fig. 2 that 'each cylinder bore i3 opens outwardly in respective concentric enlarged guide bores or spaces l3, the latter providing cross head guides for the enlarged outer ends or heads 36 of the pistons 38. These outer ends may have flat or other non-circular bearing surfaces indicated at I on circumferentially opposite sides thereof in the flange I for preventing rotation of the said ends, and the thus increased bearing surface insures that practically no driving torque is imposed on the piston and cylinder surfaces proper. The enlarged outer ends 38' of the pistons and plungers 36 carry cross pins 33, these being antifrictionally journaled in the enlarged heads on needle bearing rollers 31. The cross pins connect the pistons to the actuating reaction means, one form of which will now be described.

The actuating reaction means for the pistons comprise, as shown in Figs. 1 and 2, a pair of rings 33 and 33' disposed closely adjacent the flange I and pistons 36 on opposite sides of the plane thereof and carried by, anti-friction means, as will be hereinafter described, on an adjustable mounting including particularly a ring 32 mounted in the casing member 2! on suitable pads 25 and 23.

The free ends of the cross pins 38 extend into suitable elongated grooves, slots or notches 39 and 33 of the rings 33 and 33', the grooves of one ring. being identical with the grooves of the other so that the said free ends of the cross pins will, at the starting of the barrel 5, pick up and drive both rings in a uniform manner by abutting the end surfaces of the grooves and afterwards drive them by the rolling friction without abutting said end surfaces.

As a modification of the arrangement just described, it is possible to form flexible connections between the pumping portions of the pistons and the enlarged heads with the result that no torque is imposed on the reduced portions of the pistons or on the co-acting cylinder walls. Such flexible connections are not necessary in small units but in any event may be arranged as shown in F18. 6.

The piston proper, 36, may be formed as an independent unit and provided with a groove as at 36a forming a neck, the piston terminating in a rounded head 36b. The associated modified driving head 36' has a circular recess as at 33'a to receive the rounded head 36b, which may be maintained in said recess by an annular spring member 50. The spring member after introduction in the recess 33'a will engage through postexpansion with the neck groove 36a and an associated concentric groove provided in the lip of said recess 35a, in such manner, that, due to the slightly deformed plane of the annular spring 53, positive contact between the round head 330 and the bottom of the head recess 36's will be assured to take. up wear.

The antifrictional connection between the pins 33 and rings 33 and 33' comprise, as shown, needle bearing rollers 31, these preferably being of the cageless type and small enough and closely enough spaced to retain at all times a sufficient quantity of oil as a lubricant for the bearing. By reason of this bearing arrangement the ends of the pin'at no time slide on the peripheral surfaces of the grooves 39 with consequent loss of efficiency. points of the present arrangement is the compactness and operative rigidity and balance of the piston driving reactance members. These for greater compactness, are located as previously described, closely adjacent the pistons and flange I, being carried on antifriction bearing, preferably balls 34 and 34' in the ring 32. The outer surfaces of the rings 33 and 33' are appropriately grooved to receive the portion 34 and 34' and the two sets of balls roll in individual grooves in the adjustment ring 32. The halls are retained, each set in a two part retainer assembly 35 and 35' put together by headless screws 4| so that the entire mechanism may be taken down simply by removing the end plates 20 and 22, detaching the bearing retainer parts and then removing the rollers through, say, a single transverse channel in the ring 32, one for each ball groove as is conventional in bearing design.

The grooves 39 may be arcuate as shown in Fig. 4 or chordal as shown in Fig. and these have sufficient arcuate or chordal length to permit the full reciprocation of the pins 38 when the pump is set as in Fig. 3 for its maximum stroke. However, for starting, it is desirable that the grooves be longer than would be necessary for the above indicated purpose wherefore the barrel 5 may begin its rotation before taking up the load of the rings 33 and33'. The arcuate grooves 39 shown in Fig. 4 are easier to cut and finish grind than the chordal grooves as described in Fig. 5. The use of arcuate grooves instead of chordal changes the resultant motion of the pistons and likewise the flcwxzharacteristics of the pump. In small units the are described by the pins is only slightly divergent from the chord and thus in small units it follows that the difference does not matter materially. In larger units, on the other hand, the chordal grooves offer positive advantages in that wear between the pistons and cylinders is reduced and more uniformity in flow characteristics obtains.

One of the outstanding novel As a modification of the arrangement shown,

the reactance rings 33 and 33 may be positively synchronized other than through the medium of the cross pins 38. In other words, a series of pins, in addition to the pins 38, may positively interconnect the two reactance rings 33 and 33'. Such pins (not shown) would require cutting away the flange 1 between the individual pistons or the provision of slots of adequate size there-- tween the members 33 and 33' other than guide surfaces 1' and the pins themselves.

Each of the rings 33 and 33' is provided with a circular groove or raceway as at 41 and 41' respectively, to engage a plurality of balls 34 and 34' respectively. The grooves thus locate the rings 33 and 33' against axial displacement relative to the normally stationary shifter ring 32. The shifter ring surrounds the aforesaid rings 33 and 33 and is provided with concentrically disposed parallel spaced grooves 46 and 46' which cooperate with the grooves 41 and 41' of the inner rings 33 and 33 and the ball members 34 and 34' respectively. All these ring members are preferably made of appropriate alloy steel such as will permit proper hardening and finishing of the ball races. Each row of balls is further provided with powerful retaining rings of the separable type as at 35 and 35', these rings being separable in the mainmeridian of the balls and attachable to each other by suitable screws, preferably of the headless type. The arrangement when assembled is very similar to a radial coupling in which the driving member is the barrel and the driven members are the reactance rings 33 and 33' and the coupling elements are the pistons 36 and associated antifrictionally supported pins 38.

The circular space 8' between the peripheral surfaces of the adjustment ring 32 and the inside of the drum or casing member 2|, when the pump is in neutral position as shown in Fig. 2, is utilized for the adjustment of the ring into various operating positions for pumping fluid in either direction through the passages l8 and IS. The stroke adjustment of the pump will be accomplished by the provision of suitable control members 42 and 43 connected as by threads at 44 and 45 with the ring 32. When the reactance assembly is shifted to the position shown in Fig. 3 pumping occurs in one direction and when this assembly is shifted to the opposite side of the casing (not illustrated) reverse flow occurs.

Referring to Fig. 5 when the chordal grooves 40 and 40', in the inner adjacent faces of the rings 33 and 33', are preferred a positive synchronization of the pistons and the rings 3. and 33' is necessary. In other words, in order to maintain the proper timing between the various cycles of the individual cylinders and the ports I6 and I1 of the pintle it is necessary that in each instance the center lines of the pistons and the radial center lines of the respective chordal grooves maintain parallel positions. This requirement will be fulfilled if after the central position shown in Fig. 2, the two named center lines will rotate with equal angular speed at all times. To accomplish this synchronization, I provide a novel piston for this particular form of reactance ring construction. This form of piston is illustrated in Figs. 7 to 9. In' these figures each enlarged piston head 36, in addition to having the hole 31 for the needle rollers 31 and pin 38, is provided with a pair of laterally extending lugs 36",.one pair on each side as shown in Figs. 7 and 8. The lugs will slidably fit in the normally aligned chordal grooves 40 and 40' and couple each piston positively with the piston actuating members 33 and 33 for simultaneous rotation with the cylinders. Thus when the rings are in off 'center position relative to the barrel 5 and its' individual cylinders I 3, the dead center positions of the pistons will strictly coincide with the bridges of the pintle ports. i

Fig. 5 shows the lugs 36" slidable in the grooves 44. By providing a small amount of clearance there would not be any load transmitting contact between the lugs and the planar surfaces of the grooves but the load transmission would be confined entirely between the journal pins 33 and the planar surfaces of the grooves. Therefore the clearance between the lugs 33" and the width of the grooves is preferably such that the angular displacement of the chordal center lines of the grooves and the longitudinal axes of the lugs is at no time more than a couple of degrees. Since the piston head 36' is well guided in the large bore of the spider flange I and owing to the frictionless cooperation between the rotary and stationary rings 32, 33-43 there will be very little contact pressure between the lugs 36' and the re-acting surfaces of the grooves 40-40.

Considerable economy in construction may be accomplished and certain advantages gained by virtue of the arrangement shown in Figs. and 11. These figures show only the piston actuating parts of the mechanism and a portion of one of the pistons. The remainder of a complete unit embodying the parts shown may be in accordance with Figs. 1 and 2 for example. The adjusting ring 32', provided with suitable means includingthreaded openings 44 for shifting the same as previously described, has a central rib 56 and larger bored openings at each side thereof, each adapted to receive outer bearing race members 5| of standard antifriction bearing assemblies including inner ball race members 52, ball elements 34 and 34' and ball retainers and 35'. The outer race members may be retained in place against respective shoulders formed by the central ribs 56 by means of snap rings 53 and 53' of suitable design adapted to seat in annular grooves in the ring 32' adjacent the respective race members.

The piston actuating reactance rings 54 and 54' are properly formed to be pressed into the inner race members 52 and 52' definitely located with respect thereto by appropriate shoulders on the rings 54 and 54' for example. Figures 10 and 11 further illustrated that the normally aligned cross pin receiving grooves, indicated at 55, in the reactance rings may be continuous. In such event the reactance rings will not be positively started in rotational movement upon rotation of the impeller barrel but will nevertheless freely rotate and relieve theneedle bearing rollers 31 from too rapid movement and resultant overheating in the continued operation of the mechanism at high speed. It is advisable in this construction to increase the mass of the reactance rings 54 for fly wheel effect to maintain a constant speed of rotation in synchronization with the impeller barrel. The rings as shown are of heavier cross section than in the previously described forms.

The modifications just described offer positive advantages in reducing manufacturing cost, initial assembly and replacement of parts. Each reactance ring 54 or 54' with its entire bearing forms a complete sub-assembly which initially or as a replacement may be easily and quickly inserted into its operating position in the pump or motor and securely retained by the snap rings, the various shoulders described insuring that the parts will remain in proper axial relationship with each other.

The operation of the mechanism as a pump is as follows:

Referring to Fig. 3 for example and assuming a in one of said bell-shaped covers and projecting clockwise rotation for the impeller barrel 5 and of the associated pistons and assuming further the shifted position of the adjusting ring 32 to the left as in Fig. 3 it is evident that the pistons, which are passing the upper 180 of their rotation, are discharging into the main pump port I6, the pistons being constrained to approach the axis of the barrel 5 by reason of the eccentricity of the rings 33 and 33', whereas the pistons which are rotating on the lower 180 of their path are in communication with'the port l1 and are constrained to travel outwardly from the axis of the barrel. Consequently, the pistons will gradually draw fluid from the port ll into the cylinders as the cylinders pass said port and will subsequently discharge the fluid into the port l6.

Now when the control mechanism 42-43, etc., is shifted to the opposite side of the pump casing and assuming the same direction of rotation of the barrel, the reverse pumping action will take place, since the pistons on the upper 180 of their path will then draw fluid from the port [6 and the pistons on the lower 180 will discharge fluid from the cylinders into the port I'l. If the control arrangement is used to place all the parts concentrically as in Fig. 2, then no pumping action will result.

The antifrictionally supported pins 38 will roll at all times with reference to the piston heads so that there is never any friction between the pins and said heads, and the pins will also roll on the working surfaces of the grooves 3940, 39'4li or 55. It is evident that during the pressure cycle the pins will roll on the outer surfaces of the grooves 40 whereas during the suction cycle on the inner surfaces it is manifest that the only inertia mass which has to accelerate during travel of the pistons is the small weight of the pins as compared to relatively heavy cross heads and shoes of prior pumps of this type.

It is further evident that all of the bearing members are of the frictionless types and their successful operation does not depend on the chance of satisfactory lubrication but this operation will continue without any lubrication at all should lubrication fail for any reason. Bearing in mind that lubrication is normally afforded by oil slippage and spray of oil received thereby into the outer portion of the casing by centrifugal force, the bearings would naturally have less lubrication when the pump is operating most efficiently, that is with the least oil slippage. The smaller bearings, namely; the needle bearing 31 being of the cageless capillary type will naturally retain their supply of lubricating oil for long periods irrespective of new supply by oil slippage.

The use of the mechanism as a motor is had when fluid is forced into one or the other of the passages l8- or I9 whereupon the barrel 5 is turned as the driven member in one direction or the other depending upon the adjustment of the ring 32 tothe right or left as viewed in Fig. 3 and as will be understood from the operation of the mechanism above described acting as a pump.

Having thus described my invention,

I claim:

1. In a pump or motor in combination, a casing, comprising a pair of axially spaced bellshaped cover members and means rigidly connected therewith and completing the casing, a rotor mounted in'said bell-shaped covers and having a central cylindrical portion and an axial ,bore and counter bore, a pintle rigidly secured into sai'd casing and into said bore and counter bore and having a reduced portion forming with said bore a central valve for said rotor, said reduced portion of the pintle having just suflicient axial length to seal the pressure fluid by its viscosity in the telescoping clearance between said reduced portion and associated bore of the barrel, an impeller shaft carried by the barrel at the end opposite the pintle, a plurality of radial cylinders carried by the barrel, 2. piston carried in each of said cylinders, an enlarged head on each piston, a flange located in the plane of the pistons and having driving surfaces slidably engaglngeach of said heads, transverse bores in the piston heads, antifriction bearing means carried in said bores, circular reaction members at each side of said series of piston heads, grooves in each reaction member to receive the adjacent ends of said bearing means, and means to maintain said reaction members in spaced relation while adjustably supporting the same for governing the stroke of the pistons.

2. In a pump or'motor in combination, a casing, a stationary pintle in said casing, a rotary impeller surrounding said pintle and provided with a radial series of cylinder bores, inlet and outlet ports in the pintle adapted to communicate with said cylinder bores, pistons in said bores extending outwardly beyond the barrel, pins antifrictionally journaled in the pistons, reactance means antifrictionally journaled in the casing and having grooves in their adjacent faces adapted to receive the ends of the pins for actuating the pistons, and lugs carried on said pistons adjacent each outwardly projecting portion of said pins and received in said grooves for oscillation therealong for properly locating said reactance means during relative rotation of the said barrel and said means thereby synchronizing the movements of the pistons with respect to said ports.

3. In a radial plunger pump or motor, a rotatable barrel having a radial cylinder, a plunger reciprocable in the cylinder, a reactance means eccentric to the barrel for operating the plunger consequent upon rotation of the barrel, said reactance means comprising a stator having an annular inner operating surface surrounding the barrel with its axis parallel thereto, and providing an outer bearing race, sets. of anti-friction bearings spaced apart axially of said surface and constrained to fixed axial position thereon, axially spaced coaxial rings surrounding the barrel and disposed between the stator'and the barrel and mounted one ring in each of said sets of bearings and providing the inner race thereof and constrained to flxed axial positionthereby, said rings having parallel walls extending inwardly radially of the barrel from the zone of the bearings and spaced apart axially to accommodate therebetween a portion of the plunger, each of said 'walls having a groove extending alongside the path of travel of said portion of the plunger and opening toward the other ring,

and a crosspin anti-frictionally mounted in the plunger and extending parallel to the barrel axis,

said pin having the end portions extending be- 4. In a radial plunger pump or motor, a rotatable barrel having a radial cylinder, a plunger reciprocable in the cylinder and having a head portion, thrust means carried by the plunger head portion and extending at each end parallel to the barrel axis beyond the plunger head portion, a stator eccentric to the barrel and surrounded the barrel, sets of anti-friction bearings in the stator spaced apart axially of the stator at opposite sides of the plane ofthe plunger path, rotatable reactance rings coaxial with and lying within the stator and spaced apart axially for accommodating the plunger head portion therebetween, plunger actuating grooves in the rings opening into adjacent radial faces of the rings and accommodating the ends of the thrust means respectively for actuating the plunger in both directions of reciprocation, inner race members for the sets of anti-friction bearings respectively squeeze-fitted one onto each ring in embracing relation thereto, each race extending axially of the associated ring coextensive with the zone of the groove thereof for rotatably supporting the ring in the stator for reinforcing the associated ring against radial distortion by the thrust means.

5. In a radial piston pump or motor, a casing, a barrel having a cylinder, a plunger reciprocable in the cylinder, means rotatably mounting the barrel in the casing and comprising sets of anti-friction bearings arranged near the ends of the barrel, said barrel having an axial bore communicating with the cylinder and an enlarged counterbore at one end, a valve pintle mounted in the casing and having a portion fitting said axial bore of the barrel, said reduced portion having ports for valving cooperation with the cylinder consequent upon rotation of the barrel, and having just sufficient axial length to seal the pressure fluid by its viscosity in the telescopic clearance between said pintle portion and associated axial bore of the barrel, an impeller shaft on the end of the barrel opposite from the counterbore, means for reciprocating the piston in the cylinder consequent upon rotation of the barrel, said pintle having a portion lying within said counterbore and in spaced'relation to the circumferential wall thereof and said counterbore being positioned axially of the barrel in the same zone as the anti-friction bearings support ingthe barrel near said end.

6. In a radial plunger pump or motor, a casing,

a barrel rotatably mounted in the casing, said barrel having a cylinder, a plunger reciprocable in the cylinder, means mounting the barrel in the casing for rotation about its axis, said barrel having an axial bore communicating with the cylinder, and a coaxial enlarged counterbore ex tending from said axial bore and opening through one end of the barrel, a valve pintle mounted in the casing coaxial with the barrel and having a portion fitting said barrel axial bore, said portion having ports in valving cooperation with the cylinder as the barrel rotates, said pintle having a larger diameter portion extending from the smaller diameter portion toward the said end of the barrel and lying within said counterbore in spaced relation to the circumferential and end walls of said counterbore and there being an open uninterrupted space between said larger diameter portion of the pintle and said walls of said counterbore, an impeller shaft on theend of the barrel opposite from said counterbore, and reactance means cooperable with the plunger for reciprocating the plunger in the cylinder consequent upon rotation of the barrel and said space between the large diameter portion of the pintle and counterbore walls being suflicient to prevent contact of said walls due to the expansion of the operating parts of the pump or motor resulting from operation.

7. In a radial plunger pump or motor, a casing, a barrel rotatably mounted in the casing, said barrel having a cylinder, a plunger reciprocable in the cylinder, means mounting said barrel for rotation in the casing, said barrel having an axial bore communicating with the cylinder and a coaxial enlarged counterbore extending from said axial bore and opening through one end of the barrel, a valve pintle mounted in the casing coaxial with the barrel and having a portion fitting said barrel axial bore, said portion having ports in valvingcooperation with the cylinder as the barrel rotates, said pintle having a larger diameter portion extending from the smaller diameter portion toward the mounting of the pintle and lying within said counterbore in spaced relation to the circumferential and end wall of said counterbore, an impeller shaft on the end of the barrel opposite from said counterbore, a reactance means cooperable with the plunger for reciprocating the plunger in the cylinder consequent upon rotation of the barrel, whereby a fluid receiving chamber is formed adjacent one end of the reduced portion of the pintle for retaining fluid thereabout, said barrel mouhting means including a bearing interposed between the outer wall of the barrel and the casing and positioned axially of the barrel to lie in the zone of the barrel counterbore, whereby a small accurate clearance can be maintained between the counterbore wall and the wall of the larger portion of the pintle and said larger diameter portion of the pintle being out of supporting relation to the aligned portion of the barrel.

8. In a radial plunger pump or motor, a rotatable barrel having a radial cylinder, a plunger reciprocable radially therein, a valve pintle co operable with the cylinder consequent upon rotatlon of the barrel, said plunger having a head portion extending radially outwardly beyond the cylinder, rotatable reactance means eccentric to the barrel and having an axis of rotation parallel to the barrel axis, said reactance means having grooves disposed alongside opposite sides of the plunger head portion, thrust means carried by the plunger and extending parallel to the barrel axis and in rolling engagement to and fro in the grooves for load transmitting under rolling friction between the plunger and reactance means, and means rigid with the plunger head portion adjacent the groove engaging portions of the thrust means and extending into said grooves and in sliding engagement therewith, and cooperable with the groove walls for transmitting driving torque between the reactance means and barrel while synchronizing the movements of the cylinder with respect to the ports.

' 9. In a radial plunger pump or motor, a rotatable barrel having a radial cylinder, a plunger reciprocable in the cylinder, a reactance means eccentric to the barrel for operating the plunger consequent upon rotation of the barrel, said reactance means comprising a stator having an annular inner operating surface surrounding the barrel with its axis parallel thereto and providing an outer bearing race, sets of anti-friction bearings spaced apart axially of said surface, axially spaced co-axial rings surrounding the barrel and disposed between the stator and barrel and mounted one ring in'each of said setsuof bearings and providing the inner race thereof, said rings being spaced apart axially and accommodating a portion of the plunger therebetween, and thrust means extending parallel to the axis of rotation and connecting said plunger and rings r uciprocation of the plunger thereby and relati e oscillation of the plunger and rings along the path of rotation, said thrust means in its entirety being located between said bearings and the axis of rotation of the barrel and being spaced radiallv inward from said bearings, and said rings being independently floating circumferentially and axially relative to each other for accommodating themselves to proper operating positions with respect to their associated bearings and the thrust means.

10. In a radial plunger pump or motor, a rotatable barrel having a radial cylinder, a plunger mciprocable radially therein, valve means cooperable with the cylinder, said plunger having a portion extending outwardly beyond the cylinder, oiatable reactance means eccentric to the barrel and having an axis of rotation parallel to the L-arrel axis, said reactance means being positioned along opposite sides of said plunger portion, thrust means journalled in said plunger and rollingly engaging the reactance means and mereby connectingthe plunger to the reactance means for transmitting thrust load-between the plunger and reactance and for relative oscillation of the reactance and plunger along the path of travel, means carried by said plunger portion and engaging the reactance independently of the engagement of the latter with said thrust means for transmitting torque between said portion of the plunger and the reactance, and means on the barrel other than the wall of said cylinder cooperable with said portion of the plunger to transmit said torque therethr'ou'gh between the barrel and reactance means.

11. In a radial plunger pump or motor, a rotatable barrel having a radial cylinder; a plunger reciprocable in the cylinder; and reactance means eccentric to the barrel for operating the plunger consequent upon-rotation of the barrel, said reactance means comprising a stator having an annular inner operatingsurface surrounding the barrel and intersected by a plane which contains the axis of said cylinder and which is per-' pendicular to the axis oi rotation of the barrel,

barrel and reactance means therefor, said barrel having an axial bore, and cylinder ports opening into said bore, a stationary valve pintle having an enlarged shank portion at one of its ends and rigidly mounted by said shank portion in the housing and extending from its supporting shank .portion into said barre'l bore, the free portion being of less diameter than the shank portion and closely fitting the barrel bore, valve ports in said free portion cooperable with the ports in the said barrel bore, said barrel having an enlarged diameter counterbore extending axially inwardly from the end adjacent the pintle shank to the valve portion of the barrel bore, said pintle shank extending into said counterbore and terminating short of and in closely spaced relation to the inner end of the counterbore,- said shank being smaller in diameter than the said counterbore, there being an uninterrupted free clearance space or void of substantial radial extent between the shank and the counterbore wall, and the shank being free of operative connection to said barrel in the zone of said counterbore for permitting expansion of the pintle and barrel radially, whereby the pintle is rendered more rigid and strengthened against hydrostatic deflection of the free portion.

13. In a high pressure rotary radial plunger motor, acasing, a barrel having a central portion and hub portions near the ends thereof, sets of anti-friction bearings mounted in the casing and engaging the hub portions for mounting the barrel for rotation about its axis, said barrel having an axial bore, and having a plurality of radial, 7

cylinders in said central portion, each cylinder opening at its inner end radially into said bore, plunger-s in said cylinders, reactance means disposed between the planes of. said bearings and cooperable with the plungers for rotating the barrel, said barrel axial bore having a valve portion entirely between the planes of the, sets of bearings and having a counterbore of greater diameter extending therefrom and opening through one end of the barrel and corresponding hub portion, a pintl'e having a large rigid shank portion and mounted by said shank portion in the casing, and extending therefrom into the' ings.

mm: BENEDEK. 

